DE2804432A1 - CONTROL WITH DISC-SHAPED ROTARY VALVE ARRANGED IN A HOUSING FOR A COMBUSTION ENGINE - Google Patents

Abstract

A disc-shaped rotary slide valve (14) is arranged in a housing (8, 10). The rotary slide valve (14) has passages (32, 34, 36, 38, 39), which connect the working cylinder chamber (4) of an internal combustion engine to an air intake port (40) and an exhaust port (42) respectively. A cooling line system has coolant chambers (51, 62) in the rotary slide valve (14) and cooling ducts (60) carrying coolant from the radially inner to the radially outer part. Further coolant ducts (64) lead from the outer chambers (62) to a toroidal chamber (66). The coolant feed and discharge ducts (92 and 52) running in the housing (8, 10) lead into and out of the toroidal chambers (51, 66) of the rotary slide valve (14). Annular grooves (53, 94) of the housing (8, 10) lie opposite the toroidal chambers (51, 66) of the rotary slide valve (14). The simple construction permits more intensive cooling. <IMAGE>

Description

PATENTANWÄLTE file number

DIPL.-1NG. CONRAD KÖCHLING, Γ. 2QQL 1 * 3?

. CONRAD-JOACHIM KÖCHUNG ^{Note :} | * | ^old " ^Μαπ "

ο β «= ™« U ^{υίει Μ} ° π * β Tabor B

Fleyer Strasse 135, 5800 Hagen

Call (0 23 31) 81164

Telegrams: Patentköchling Hagen «,. , • r * _L * · \

Accounts: Commerzbank AG. Hagen 6512 GiubiaSCO (enamel)

(BLZ 45040042) 35150 »

Sparkasse Hagen 100 012 043 Postal check: Dortmund 5969-460

Serial No £ 9.! * 2 / JB

4 «February - 497a

Control with a disc-shaped rotary slide valve for an internal combustion engine arranged in a housing

The present invention relates to a control with a disc-shaped rotary slide valve arranged in a housing for an internal combustion engine, which is provided with passages, the at least one working cylinder space with a or several air intake ducts bzin. one or more Connect exhaust gas exhaust ducts, uiobei for cooling the Housing and the rotary valve in the housing and rotary valve

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one with an outside of the rotary valve Cooling line system connected to a vacuum point is provided, which coolant chambers in the rotary valve and from the radial side having inner to radially outer parts coolant leading cooling channels.

The present invention represents a further development of the invention disclosed in CH-PS 575 071 the above-mentioned invention posed the problem of simpler construction of such in practice Control, combined with more intensive cooling, without however such advantages through newly emerging Having to buy disadvantages.

This problem is solved by the present control, which is characterized by the wording of the characterizing part of Claim 1 distinguishes.

The control according to the invention will then be explained using a drawing, for example. Show it:

Fig. 1 shows the upper part of a in longitudinal section along the cutting line I - I shown cylinder head with attached, disc-shaped arranged in a housing Rotary valve with from the rotary valve

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broken parts,

FIG. 2 shows a section through the control according to FIG. 1, according to Section line II - II

3 shows a section analogous to that according to FIG. 2 through another embodiment of a controller

Fig. 4 excerpts from radial cuts through rotary valve and 5

to show the routing of the cooling channels, in

two different versions.

In Figs. 1 and 2, part of a cylinder head 2 is a Four-stroke internal combustion engine with a working cylinder space shown. A housing 6 is arranged, e.g. screwed, on the cylinder head 2. This comprises two housing halves 8 and 10, which are held together e.g. by screws.

Located between these two housing halves 8 and 10
A disk-shaped rotary slide valve 14. Its shaft 16 is located on the one hand in the housing half 10 in a bearing 19 which absorbs radial and axial forces and on the other hand in the housing half 8 in a plain bearing 21 which only absorbs radial forces.

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From the working cylinder space 4 one leads in the direction of rotation of the rotary valve 14 displaced, with respect to the axis of the shaft 16 eccentrically arranged bore 22 through the cylinder head 2 to the housing 6. In this bore 22 is a spring-loaded sealing shoe 24 with a passage 26. A cylindrical pin 28 - part of the sealing shoe 24 - is provided with an inner sealing ring 30 provided. The cylinder head 2 has recesses 33 radially outside the bore 22 for receiving helical springs 35 on. The sealing shoe 24 is resiliently pressed against the rotary valve 14 on these helical springs 35, supported.

The rotary valve 14 has three pairs (a total of six) passages 32, 34, 36, 37, 38 and 39, each offset by 120 ° inform of 90 manifolds, which the end face 18 and one or the other lateral surface 20 of the rotary valve 14 connect with each other. In the corresponding position of the rotary valve 14, one connects each of the inlet passages 32, 36 or 38, a suction bore 40 located in the housing half 10 with the passage 26 in the sealing shoe 24. The rotary valve contains approximately 40 offset from the air intake passages 32, 36, 38 14 also the three outlet passages 34, 37, 39, which connect the passage 26 with the one in the housing

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Connect half 8 lying Äbgasausstosskanal 42. the Cross-sections of the passages 32, 34, 36, 37, 38 and 39 are approximately on the lateral surface 20 of the rotary valve 14 rectangular, whereas the corresponding cross-sections on the end faces 18 of the rotary valve 14 are approximated are kidney-shaped. The intake bore 40 and the exhaust gas outlet channel 42 have a circular cross section.

The mentioned connections by means of the passages 32, 36, 38 between the suction bore 40 and the passage 26 on the one hand and the connections by means of the passages 34, 37, 39 between the passage 26 and the On the other hand, exhaust gas outlet ducts 42 are only guaranteed in corresponding positions of rotary slide valve 14. In Pig, 1 is the exhaust gas emission position of the rotary valve 14 shown. In all other positions, the sealing shoe 24 with its support surface 46 ensures for the required sealing of the cylinder space 4 to the outside.

The following is provided for cooling the rotary valve 14 and the exhaust gas outlet duct 42:

The housing half 10 is, as FIG. 2 shows, with a coolant supply bore 92, which opens into an annular groove 9. Opposite this is an analog annular groove 51 of the

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Rotary slide 14. Coolant channels 60 lead out of the annular groove 51 - evenly distributed in groups in the slide 14 from the inside to the outside. They open into spaces 62 which, for example, as FIGS. 1 and 2 show, as recesses parallel to the axis of rotation or bores 62 can be formed. The outlets of these bores 62 open into coolant channels 64, which lead radially from the outside to the inside, the recesses 62 with a further annular groove 66 near the axis Connect area of rotary valve 14. The annular groove 66 feeds another annular groove 53 provided in the housing 8. The annular groove 53 in turn feeds a recess via a segment-shaped channel 52, which after the installation of the Exhaust gas outlet channel 42 has an elongated annular space 58 forms. The space 58 is connected via a passage 57 to a vacuum point, preferably of the engine.

It was recognized that with a multi-cylinder engine design the coolant supply through the main shaft is unfavorable. For this reason, the one shown in FIG apparent lateral coolant supply bore 92 is provided in the housing 10. It should be noted that the Annular groove 94 surrounds the elastic sealing ring 96 and prevents it from overheating.

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. 77.

Rings 79, 81, 82 protruding from the end faces 18 of the rotary valve 14 or inserted therein are shown in FIG corresponding grooves of the two housing halves 8 and 10 and form labyrinth seals. The rotary valve 14 does not touch either of the two enclosing it Housing halves 8 and 10 metallic.

A hole 87 in the housing 8, 10 is used to receive an oil strainer 89 designed as a lubricating wick. This hole 87 is tangent to the housing recess for the rotary valve 14 in such a way that the oil strainer 89, which oil from the lubrication network the internal combustion engine receives this on a narrow Surface line surface on the surface 20 of the rotary valve 14 gives up. Since the spring-loaded sealing shoe 24, at least in the area of its bearing surface 46, is made of self-lubricating Metal, for example a self-lubricating bronze, can exist, so here too the frictional resistance is at optimal sealing reduced to a minimum.

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The rotary valve 14 described, if it is used with a four-stroke internal combustion engine to control it, is coupled to the latter in such a way that the rotary valve corresponds to the three inlet and the three outlet passages 32, 34, 36, 37, 38 and 39 per working cycle, ie with two revolutions of the crankshaft of the engine, V executes 3 revolutions. The reduction ratio is therefore 6 to 1.

For manufacturing reasons, it can be advantageous to cast the inner part of the rotary valve 14 and to shrink a ring band 15 onto this part. This not only simplifies the machining of the rotary valve 14, but also created the possibility of 15 different materials for the inner part and the ring band to use.

The control described works in connection with a four-stroke internal combustion engine in the following way:

In the position shown in FIGS. 1 and 2, the piston of the internal combustion engine is in the exhaust stroke, in which the explosion gases after their pressure-related energy has been released to the piston of the internal combustion engine from the working cylinder space 4 are ejected.

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This discharge occurs through the passage 26 and the outlet passage 34 into the exhaust gas discharge channel 42, from where the exhaust gases flow into the open.

During the subsequent intake stroke, the working piston moves down from its top dead center position in the cylinder chamber 4. The rotary valve 14 has rotated further (in the direction of the arrow according to FIG. 1), with the intake passage now 32 in the rotary valve 14 has an ever-increasing passage to the passage 26 and to the suction bore 40 releases. The formation of a negative pressure in the working cylinder space 4, e.g. by the engine piston, therefore the outside air through the intake bore 40 into the air intake passage 32 and from this through the passage 26 sucked into the working cylinder space 4. This takes time so long until the rear edge of the suction passage 32 the front edge of the suction hole 40 or that of the Passage 26 sweeps over and therefore the working cylinder space 4 is closed to the outside, whereupon the filling process of the working cylinder space 4 is ended.

In the subsequent compression stroke, the piston compresses the combustion air sucked in in the working cylinder space 4, fuel is injected into the compressed air at the appropriate moment, so that an explosive Mixture is created.

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■ Η-

It is of course also possible for the suction bore 40 to have a corresponding one Carburetor to be connected upstream, so that no longer pure air through the above-described channels into the working cylinder space 4, but a gasoline vapor-air mixture.

Shortly before the piston reaches top dead center, this mixture is ignited and deflagrated by means of a spark plug, the resulting pressure pushes the piston down while it delivers power to the crankshaft. This is the work cycle. During this time, the rotary valve 14 must seal off the working cylinder space 4 so that the deflagration gases do not occur under their high pressure through the cylinder head and the housing 6 to the outside uselessly deflagrated. the end For this reason, the sealing shoe 4 is resiliently arranged in the cylinder head 2 so that it has the option of under the Pressure in the working cylinder space 4 and the additional pressure of the coil springs 35 with its sealing surface 46 on the rotary valve 14 to lie tightly. The self-lubricating metal ensures that at least the area is made of the sealing surface 46 of the sealing shoe 24 is made, for the friction and thus the wear and the lost To keep performance as low as possible. Sealing takes place by means of the sealing ring 30.

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At the end of the work cycle, when the piston is in its lower position Is dead center, the rotary valve 14 has continued to rotate in such a way that now during the subsequent exhaust stroke, the initially has been described, the connection of the working cylinder space 4 via the passage 26 with the outlet passage 34 and the exhaust gas outlet channel 42 is restored.

It is obvious that the control system explained is very high is subjected to thermal stresses, which is particularly the case for the rotary slide valve 14 rotating in the housing halves 8, 10 with the shaft 16 and the sealing shoe 24 as well as the exhaust gas outlet channel 42 applies. Therefore, these parts must be particularly good, i. intensively and safely cooled so that no temperature peaks occur. To this end, got through the negative pressure in the crankcase or another pump source, cooling air through the channels 60, 62 and 64 into the annular groove 66 of the rotary valve 14, which faces the other annular groove 53 in the housing 8.

The cooling air leaves this chamber 53 through the channel 52, from where it flows into the annular space 58.

The lateral surface 20 of the rotary valve 14 is lubricated accordingly by means of the lubricating wick made from a sieve 89, while between the inner wall of the housing half 8 and the rotary valve 14 or its corresponding end face

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18 a sealing layer of soot is formed by the exhaust gases, which naturally improves the whole system seals.

Another embodiment of such a control can be seen in FIG.

Here is part of a cylinder head 101 of a four-stroke internal combustion engine shown with a working cylinder chamber 103. A housing 107 is arranged on the cylinder head 101, e.g. screwed on. This comprises two housing halves 109 and 111 which are held together, e.g. by screws will.

Located between these two housing halves 109 and 111 A disk-shaped rotary slide valve 115 is located. Its shaft 117 is mounted in the housing halves 109 and 111.

From the working cylinder space 103 leads with respect to Axis of the shaft 117 eccentrically arranged bore 123 through the cylinder head 101 to the housing 107. In this Bore 123 is a spring-loaded sealing shoe 125 with a passage 127. It is of a known nature.

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The rotary valve 115 also has three pairs (a total of six) offset by 120 passages 137, 139 in the form of 90 bends, which connect the lateral surface 118 and one or the other end face 113 or 114 of the rotary valve to one another. The three air intake passages 137, offset by 120 to each other, each connect a suction bore 141 located in the housing half 111 with the passage 127 in the sealing shoe 125. The rotary valve 115 also contains the three outlet passages 139, which are offset by approximately 40 to the air intake passages 137 Connect 127 to the exhaust gas discharge duct 143 located in the housing half 109. The cross-sections of the passages 137 and 139 are approximately rectangular on the outer surface of the rotary valve 115 , whereas the corresponding cross-sections on the end faces 113 and 114 of the rotary valve 115 are approximately kidney-shaped. The intake bore and the exhaust gas outlet duct 143 have an approximately circular cross-section.

The mentioned connections by means of the passages 137 between the suction bore 141 and the passage 127 of a on the one hand and the connections by means of the passages 139 between the passage 127 and the exhaust gas outlet duct 143 on the other hand are only in the corresponding positions of the rotary

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Slider 115 guaranteed.

In FIG. 3, the slide 115 is in the working cycle, i.e. before the exhaust gas discharge position of the rotary slide 115.

The following is provided for cooling the rotary valve 115 and the exhaust gas outlet duct 143:

The shaft 117 is provided with a central, axial coolant supply bore 145 and a drainage hole 148, which are separated from one another by a transverse web. Corresponding the coolant channels 161, 162 and 164 arranged between the six passages 137, 139 are shown in FIG of the shaft 117 lateral connection bores to the bores 145 and 148 are provided, which the coolant flow in the Secure slide 115. The channels 161 and 164, like the channels 60 and 64, can promote flow in the slide 115 be arranged. The cooling can be done here by water, oil or the like. She is apart from the shaft connections, completely leak-free.

In this embodiment, a second cooling system is provided, which is a hub part of the rotary valve 115 and then the exhaust gas discharge duct 143 or the latter Channel-defining insert cools. The coolant is fed in via a housing bore 192,

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which opens into an annular chamber 19 4. This continues in an annular chamber 151, as FIG. 3 clearly shows. Of the Chamber 194 passes the coolant through at least one, for example ring segment-shaped, bore in an annular space 152, which surrounds the wall of the channel 143 directly and causes it to be intensively cooled. The coolant then passes through a channel 157 in the cylinder head 101 to a suction point, e.g. in the engine housing.

The arrangement of this cooling system results in such intensive cooling that the two sealing rings 196 Can be produced as so-called cold engine sealing rings from material that is only resistant up to approx. 110 ° C.

In order to limit the heating of the rotary valve 115 to a minimum, that is swept by the exhaust gases The surface in the slide 115 is designed to be minimal by its profiling, as is its cross-section with the triangular shape Annular groove 113 can be clearly seen. The above-mentioned area in the slide 115 is thereby reduced by about a third,

Rings 179 and 181 protruding from the end faces 113 and 114 of the rotary valve 115 are in corresponding Grooves of the two housing halves 109 and 111 in front and form Labyrinth seals, the rotary valve 115 touches

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Incidentally, neither of the two halves of the housing surrounding it 109 and 111.

Here, too, a hole in the housing 109, 111 of the receptacle an oil strainer designed as a lubricating wick. This hole is tangent to the housing recess for the rotary valve 115, as explained in detail for FIG. 1. Since the spring-loaded sealing shoe 125, at least in the area of its contact surface 144, made of self-lubricating metal, such as a self-lubricating bronze, is the same here the frictional resistance is reduced to a minimum with an optimal seal.

The rotary valve 115 described is used for controlling a four-stroke internal combustion engine when it is used is coupled to this in such a way that the rotary valve 115 corresponds to the three inlet and the three outlet passages 137 and 139 per work cycle, i.e. with two crankshaft revolutions of the engine, executes V3 revolutions. The reduction ratio is therefore 6 to 1.

The control described works in connection with a four-stroke internal combustion engine basically analogous to this for the execution according to FIGS. 1 and 2 is explained.

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In FIGS. 4 and 5, two further possibilities can be seen of how coolant is introduced into a rotary valve can be.

Thus, Fig. 4 shows a shaft 217, with one, the coolant supplying axial bore 245 and an analogous leading away axial bore 248. Through corresponding lateral The coolant passes through openings in the shaft via the coolant channels 261, 262 and 264 into the outflow bore 248. Here, too, a ring 150 is pulled, e.g. shrunk, onto the inner body of the rotary valve 215.

FIG. 5 shows another possibility of guiding the coolant, with a shaft 317 of the rotary valve 315. Here is one axial supply bore 345 is provided for the coolant, which via lateral passages in correspondingly in the inner body of the rotary valve 315 guided channels 361, 362 and arrives. As a drainage opening in the rotary valve 315 is here a partial annular groove 366 is provided, which is opposite an annular groove in the stator (not shown.)

These examples show that the arrangement of the coolant channels in rotary valves leads to such a control can be done in many ways, and in the end corresponding attempts are made in every respect, i.e. both

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In terms of production technology and cooling technology, they are optimal Need to reveal the solution.

In this sense, detailed tests have shown that the explained Type of coolant routing, in particular guiding the coolant around in the rotary valve 14 from the inside to the outside and again inwardly leading coolant channels or recesses not only a substantial simplification in the Production, but also brings better cooling of the relevant parts. The figures show possibilities, for example the coolant flow in rotary valves. These channels form (between the passages for inlet and outlet of the engine gases) channel groups, which are symmetrical in the rotary valve and therefore, according to the number of groups, a more even one able to ensure thermally little location-dependent temperature. This in turn allows a higher thermal Load capacity of the rotary valve, which, at least theoretically, increases with the number of passes in the rotary valve. Ever according to the number of passage groups, of course, the diameter must be of the rotary valve can be enlarged accordingly.

The cooling system can be charged with liquid, air or any other medium. The overpressure or underpressure, which is necessary to set the fluid in motion, can preferably be provided by the motor itself or by someone attached to the motor.

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closed aggregate can be generated.

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Claims (12)

Claims 1. ι control with arranged in a housing disc-shaped rotary valve for an internal combustion engine, which is provided with passages that connect at least one working cylinder chamber with one or more air intake ducts or one or more exhaust gas discharge ducts, for cooling the housing and the rotary valve in the housing and rotary valve a cooling line system connected to a vacuum point outside the rotary valve is provided, which has coolant chambers in the rotary valve and cooling channels leading coolant from radially inner to radially outer parts, characterized in that further coolants leading radially from the outer to the inner parts, from at least one of the Coolant chambers (62, 162, 262, 362) opening cooling channels (64, 164, 264, 364J are arranged. 2. Controller according to claim 1, characterized by at least one coolant supply running in the housing (8, 10) (92) and discharge channel (52) which open into and out of annular chambers (51, 66) of the rotary valve (14). 3. Control according to claim 1, characterized in that the from the outer to the inner parts of the rotor (14) - 21 - 909832/0098 Coolant-carrying channels (64) on one end face of the rotary valve open annular groove (66) are connected. 4. Control according to claim 1, characterized in that that the coolant-carrying channels in the rotary valve are arranged in a U-, V-, W- or X-shape. 5. Control according to claim 1, characterized in that coolant channels are provided in the rotating part, such that that coolant flows from the hollow shaft into the rotary valve and from there back into the hollow shaft. (Figures 3, 4). 6. Control according to claim 3, characterized in that the annular chambers (51, 66) of the rotary valve (14) have annular grooves (53, 94) of the housing (8, 10) are opposite. 7. Control with arranged in a housing disc-shaped Rotary slide valve for an internal combustion engine, which is provided with passages that have at least one working cylinder space one or more air intake ducts or one or connect a plurality of exhaust gas discharge ducts, with one for cooling the housing and the rotary valve in the housing and rotary valve a cooling line system connected to a vacuum point outside the rotary valve is provided, which in the rotary valve coolant chambers and from radially inner ones - 22 - 909832/0098 has cooling channels leading to the radially outer parts of the coolant, characterized in that the rotary slide valve consists essentially of an inner body and a cover ring (150; 116) applied to it peripherally. 8. Control according to claim 1 or claim 7, characterized characterized in that the rotary valve (14, 115, 215, 315) consists at least in parts of cast. 9. Control according to claim 1 or claim 7, characterized in that that the rotary valve has a groove formed in one end face in order to connect the heat exchange surface with the To reduce exhaust gases. (Fig. 3) 10. Control according to claim 1 or claim 7, characterized in that that the exhaust gas discharge duct (143) is provided with a partially cooled, preferably exchangeable, insert is fixed. 11. Control according to claim 1 or 7, characterized in that elastic sealing rings (96, 196) of the Coolant chambers (51, 53, 194) are completely surrounded to protect them from overheating. 909832/0098 - 23 - 12. Control according to claim 7, characterized in that the cover ring (116, 150) is shrunk on. Dip! -Inc. Con-s- 'Schli 909832/0098